AU2003203417A1

AU2003203417A1 - Centre Bearing Assembly Including a Support Member Containing a Rheological Fluid

Info

Publication number: AU2003203417A1
Application number: AU2003203417A
Authority: AU
Inventors: James A Duggan; Scott B Robb
Original assignee: Dana Inc
Current assignee: Dana Inc
Priority date: 2002-04-04
Filing date: 2003-04-01
Publication date: 2003-10-23
Also published as: EP1355070A2; US6960024B2; EP1355070A3; US20040022467A1; BR0300859A

Description

i L S&F Ref: 631324

AUSTRALIA

PATENTS ACT 1990 COMPLETE SPECIFICATION FOR A STANDARD PATENT Name and Address of Applicant: Actual Inventor(s): Address for Service: Invention Title: Dana Corporation 3222 West Central Avenue Toledo Ohio United States of America Scott B. Robb James A. Duggan Spruson Ferguson St Martins Tower Level 31 Market Street Sydney NSW 2000 (CCN 3710000177) Centre Bearing Assembly Including a Support Member Containing a Rheological Fluid The following statement is a full description of this invention, including the best method of performing it known to me/us:- 5845c

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Centre Bearing Assembly Including a Support Member Containing a Rheological Fluid Background of the Invention This invention relates in general to bearings for supporting shafts for rotation. In particular, this invention relates to an improved structure for a centre bearing assembly for rotatably supporting an intermediate portion of a vehicle driveshaft assembly.

In most land vehicles in use today, a drive train system is provided for transmitting rotational power from an output shaft of an engine/transmission assembly to an input shaft of an axle assembly so as to rotatably drive one or more wheels of the vehicle. To accomplish this, a typical vehicular drive train system includes a driveshaft assembly having first and second end fittings (such as tube yokes) that are secured to the opposed ends thereof The first end fitting forms a portion of a first universal joint, which provides a rotatable driving connection from the output shaft of the engine/transmission assembly to the first end of the driveshaft assembly while accommodating a limited amount of angular misalignment between the rotational axes thereof. Similarly, the second end fitting forms a portion of a second universal joint, which provides a rotatable driving connection from the second end of the driveshaft assembly to the input shaft of the axle assembly while accommodating a limited amount of angular misalignment between the rotational axes thereof.

In some vehicles, the distance separating the engine/transmission assembly and the axle assembly is relatively short. For these vehicles, the driveshaft assembly can be formed from a single, relatively long driveshaft tube having the first and second end fittings secured to the ends thereof In other vehicles, however, the distance separating the engine/transmission assembly and the axle assembly is relatively long, making the use of a single driveshaft tube impractical. For these vehicles, the driveshaft assembly can be formed from a plurality (typically two) of separate, relatively short driveshaft sections. In a compound driveshaft assembly such as this, a first end of the first driveshaft section is connected to the output shaft of the engine/transmission assembly by a first universal joint, a second end of the first driveshaft section is connected to a first end of the second driveshaft 3o section by a second universal joint, and a second end of the second driveshaft section is connected to the input shaft of the axle assembly by a third universal joint.

A compound driveshaft assembly that is composed of two or more separate driveshaft sections usually requires the use of a structure for supporting the intermediate portions thereof for rotation during use. A typical intermediate support structure for a driveshaft assembly (which is typically referred to as a centre bearing assembly) includes an annular bearing having an inner race that engages one of the driveshaft sections and an outer race that supports the inner race for rotation relative thereto. The outer race of the annular bearing is supported within a generally annular support member that is usually formed from a relatively resilient material, such as rubber. The resilient support member is, in turn, PALSpecifications/631324specilklp supported within a rigid bracket that is secured to a support surface provided on the vehicle.

Thus, the centre bearing assembly functions to support the intermediate portion of the driveshaft assembly for rotation during use. Many centre bearing assembly structures of this general type are known in the art.

As is well known, the engine/transmission assembly of a typical vehicular drive train system generates a variety of torsional and other relatively high frequency vibrations in the driveshaft assembly as it is rotated during use. Such driveshaft assembly vibrations often result in the generation of noise that can undesirably be transmitted into the vehicle. The resilient support member is provided in the centre bearing assembly to absorb at least some of such vibrations so as to reduce the amount of noise that is transmitted from the driveshaft assembly to the vehicle frame. To accomplish this, the resilient support member is usually formed from an elastomeric material, such as rubber, having a resonant frequency that is approximately the same as the frequency of the vibrations that are generated in the driveshaft assembly. When the resonant frequency of the resilient support member is is approximately the same as the frequency of the noise and other vibrations in the driveshaft assembly, then such noise and other vibrations will be substantially absorbed by the resilient support member and will not transmitted to the vehicle frame during use.

However, it has been found that the resonant frequency of the resilient support member may not always be approximately the same as the frequency of the noise and other vibrations in the driveshaft assembly. For example, it has been found that changes in the ambient temperature of the resilient support member can cause the resonant frequency thereof to vary. However, the torsional and other relatively high frequency vibrations that are generated by the engine and the transmission in the driveshaft assembly as it is rotated during use remain relatively constant. If the resonant frequency of the resilient support member is not approximately the same as the frequency of the noise and other vibrations in the driveshaft assembly, then the ability of the resilient support member to absorb such noise and other vibrations will be adversely affected. Thus, it would be desirable to provide a resilient support member for a centre bearing assembly having a resonant frequency that can be adjusted in accordance with changes in the operating conditions of the vehicle such that the resonant frequency of the resilient support member is always approximately the same as the frequency of the noise and other vibrations in the driveshaft assembly.

Therefore, noise and other vibrations will be substantially absorbed by the resilient support member and will not transmitted to the vehicle frame during use.

Summary of the Invention This invention relates to an improved structure for a centre bearing assembly for rotatably supporting an intermediate portion of a vehicle driveshaft assembly during use.

The centre bearing assembly includes a rigid bracket that is secured to a support surface of the vehicle, a support member that is supported within the rigid bracket, and an annular bearing that is supported within the support member for rotatably supporting the PALSpefcatons631324specAkp intermediate portion of the vehicle driveshaft assembly. The support member is formed from a resilient material and has a cavity formed therein. A sponge is disposed within the cavity formed in the support member. The sponge may be formed from any material that is capable of absorbing or otherwise retaining a quantity of a rheological fluid therein. A control circuit is provided for selectively generating and applying an energy field to the rheological fluid contained within the sponge and thereby varying the resistance to flow or shear thereof As a result, the vibration dampening characteristics of the support member can be varied.

Various objects and advantages of this invention will become apparent to those skilled in the art from the following detailed description of the preferred embodiment, when read in light of the accompanying drawings.

Brief Description of the Drawings Fig. 1 is a side elevational view of a drive train system for a vehicle including a centre bearing assembly in accordance with this invention.

Fig. 2 is an enlarged sectional elevational view of a portion of the centre bearing assembly illustrated in Fig. 1.

Fig. 3 is a sectional elevational view of the centre bearing assembly taken along line 3-3 of Fig. 2, wherein the bracket and the electromagnetic coil have been omitted for clarity.

Fig. 4 is a block diagram of a control system for the centre bearing assembly illustrated in Figs. 1 through 3.

Detailed Description of the Preferred Embodiment Referring now to the drawings, there is illustrated in Fig. I a drive train system, indicated generally at 10, for a vehicle that is adapted to transmit rotational power from an engine/transmission assembly 11 to a plurality of driven wheels (not shown). The illustrated drive train system 10 is intended merely to illustrate one environment in which this invention may be used. Thus, the scope of this invention is not intended to be limited for use with the specific structure for the vehicle drive train system 10 illustrated in Fig. 1 or, for that matter, to vehicle drive train systems in general. On the contrary, as will become apparent below, this invention may be used to support any desired component for rotation.

0so The engine/transmission assembly 11 is conventional in the art and includes an externally splined output shaft (not shown) that is connected to a first slip yoke, indicated generally at 12. The first slip yoke 12 is conventional in the art and includes an end portion 13 having a smooth cylindrical outer surface and an internally splined inner surface. The internally splined inner surface of the end portion 13 of the first slip yoke 12 engages the externally splined output shaft of the engine/transmission assembly 11 in a known manner.

As a result, the first slip yoke 12 is rotatably driven by the output shaft of the engine/transmission assembly 11, but is free to move axially relative thereto to a limited extent.

PALSpecificaUoas/631324speciklp An annular seal 1 la may be provided within or adjacent to the end of the engine/transmission assembly 11. The end portion 13 of the first slip yoke 12 extends through the annular seal 1 Ia. In a known manner, the seal 11 la engages and seals against the smooth outer cylindrical surface of the end portion 13 of the first slip yoke 12 to prevent s dirt, water, and other contaminants from entering into the engine/transmission assembly 11.

The seal 11 a is conventional in the art and can be formed having any desired structure. To insure a reliable seal, however, it is usually important for the outer cylindrical surface of the end portion 13 of the first slip yoke 12 to be generally smooth and free from relatively large surface irregularities, such as nicks and dents. If desired, the seal 11 a may be retained in an annular ridge (not shown) formed in the engine/transmission assembly 11.

The first slip yoke 12 further includes a yoke portion 14 that forms one part of a first universal joint assembly, indicated generally at 15. The first universal joint assembly 15 is also conventional in the art and includes a tube yoke 16 that is connected to the yoke portion 14 of the first slip yoke 12 by a cross in a known manner. The tube yoke 16 is secured, such as by welding, to a first end of a first driveshaft section 17 for rotation therewith. The first universal joint assembly 15 thus provides a rotational driving connection between the output shaft of the engine/transmission assembly 11 and the first driveshaft section 17, while permitting a limited amount of axial misalignment therebetween.

The first driveshaft section 17 extends through and is supported for rotation by a centre bearing assembly, indicated generally at 20. The structure of the centre bearing assembly 20 will be explained in detail below. The centre bearing assembly 20 is secured to a support surface 22, such as a portion of a frame, chassis, or body of the vehicle. The first driveshaft section 17 has a second end 23 that, in the illustrated embodiment, is reduced in diameter relative to the first end of the first driveshaft section 17, although such is not necessary. The reduced diameter end 23 can be formed as a separate structure that is welded onto the larger diameter first end of the first drive shaft section 17. In any event, a portion of the outer surface of the reduced diameter second end 23 of the first driveshaft section 17 is formed having a plurality of external splines (not shown).

A second slip yoke, indicated generally at 25, is connected, such as by welding, to the reduced diameter second end 23 of the first driveshaft section 17 for rotation therewith. The second slip yoke 25 is conventional in the art and includes an end portion 26 having an internally splined inner surface (not shown). The internally splined inner surface of the end portion 26 of the second slip yoke 25 engages the externally splined portion of the second end 23 of the first driveshaft section 17 in a known manner. As a result, the second slip yoke 25 is rotatably driven by the first driveshaft section 17, but is free to move axially relative thereto to a limited extent.

An annular seal, indicated generally at 28, may be mounted on the end portion 26 of the second slip yoke 25. The reduced diameter second end 23 of the first driveshaft section 17 extends through the annular seal 28. In a known manner, the annular seal 28 engages and seals against the smooth outer cylindrical surface of the reduced diameter second end 23 PALSpecificaoarS/631 324specilp of the first driveshaft section 17 to prevent dirt, water, and other contaminants from entering into the region of the cooperating splines. The seal 28 is conventional in the art and can be formed having any desired structure.

The second slip yoke 25 further includes a yoke portion 27 that forms one part of a second universal joint assembly, indicated generally at 30. The second universal joint assembly 30 is also conventional in the art and includes a tube yoke 31 that is connected to the yoke portion 27 of the second slip yoke 25 by a cross in a known manner. The tube yoke 31 is secured, such as by welding, to a first end of a second driveshaft section 32 for rotation therewith. The second universal joint assembly 30 thus provides a rotational driving connection between the second end 23 of the first driveshaft section 17 and the first end of the second driveshaft section 32, while permitting a limited amount of axial misalignment therebetween.

The second end of the second driveshaft section 32 is secured, such as by welding to a tube yoke 33 that forms one part of a third universal joint assembly, indicated generally at 34. The third universal joint assembly 34 is also conventional in the art and includes a third slip yoke, indicated generally at 35. The third slip yoke 35 is conventional in the art and includes a yoke portion 36 that is connected to the tube yoke 33 by a cross in a known manner. The third slip yoke 35 further includes an end portion 37 having a smooth cylindrical outer surface and an internally splined inner surface (not shown). The internally splined inner surface of the end portion 37 of the third slip yoke 12 engages an externally splined input shaft (not shown) of a conventional axle assembly 38 that is connected to the plurality of driven wheels of the vehicle in a known manner. As a result, the input shaft of the axle assembly 38 is rotatably driven by the second driveshaft section 32, but is free to move axially relative thereto to a limited extent.

An annular seal (not shown) may be provided within or adjacent to the end of the axle assembly 38. The annular seal may be similar in structure and operation to the annular seal 1 la described above. The end portion 37 of the third slip yoke 35 extends through the annular seal. In a known manner, the annular seal engages and seals against the smooth outer cylindrical surface of the end portion 37 of the third slip yoke 35 to prevent dirt, water, and other contaminants from entering into the axle assembly 38. The seal is conventional in the art and can be formed having any desired structure. To insure a reliable seal, however, it is usually important for the outer cylindrical surface of the end portion 37 of the third slip yoke 35 to be generally smooth and free from relatively large surface irregularities, such as nicks and dents. If desired, the seal may be retained in an annular ridge (not shown) formed in the axle assembly 38.

Referring now to Figs. 2 and 3, the structure of the centre bearing assembly 20 is illustrated in detail. As shown therein, the centre bearing assembly 20 includes a rigid bracket or frame 41 that is secured to the support surface 22 of the vehicle. Typically, the bracket 41 has a generally U-shaped body portion having respective flange portions (not shown) extending outwardly from the ends thereof. Threaded fasteners (not shown) can PALSpecifications631324specVklp extend through respective apertures formed through the flange portions to secure the bracket 41 to the support surface 22 of the vehicle. If desired, the body portion of the bracket 41 can be formed having a generally U-shaped cross sectional shape, as shown in Fig. 2, to increase the strength and rigidity thereof.

s The centre bearing assembly 20 also includes a support member 42 that is supported within the rigid bracket 41. The support member 42 is generally annular in shape and is preferably formed from a resilient material, such as a conventional elastomeric material (rubber, for example) of the type that is typically used in conventional centre bearing assemblies. The support member 42 has a cavity 42a formed therein that, in the illustrated embodiment, is a generally annular recess that extends circumferentially about the inner portion of the support member 42. However, the cavity 42a may be formed having any desired shape and may, if desired, be formed completely enclosed within the support member 42. If desired, the support member 42 can have a rigid support ring 43 secured thereto. In the illustrated embodiment, the support ring 43 is formed from an annular band of a metallic material and is moulded to an inner portion of the support member 42.

However, the support ring 43 can be formed having any desired shape and can be formed from any desired material.

The centre bearing assembly 20 further includes a sponge 44 that is disposed within the cavity 42a formed in the support member 42. In the illustrated embodiment, the sponge 44 has a generally circular cross sectional shape and extends circumferentially throughout the entire extent of the annular cavity 42a. However, it will be appreciated that the sponge 44 can be formed having any desired shape and need not extend completely throughout the annular cavity 42a. Furthermore, it will be appreciated that a plurality of individual sponges 44 may be disposed within the cavity 42a instead of a single continuous sponge 44, as shown in Fig. 3. The sponge 44 may be formed from any material that is capable of absorbing or otherwise retaining a quantity of a fluid therein, for a purpose that will be explained in greater detail below. For example, the sponge 44 may be formed from a conventional open cell foam material, such as polyethylene. However, the sponge 44 may be formed from any other desired material.

If desired, a retaining and positioning member 45 can be provided within the cavity 42a of the support member 42. In the illustrated embodiment, the retaining and positioning member 45 is disposed radially inwardly of the sponge 44 and extends circumferentially throughout the entire extent of the annular cavity 42a. However, it will be appreciated that the retaining and positioning member 45 need not extend completely throughout the annular 3s cavity 42a. Furthermore, it will be appreciated that a plurality of individual retaining and positioning members 45 may be disposed within the cavity 42a instead of a single continuous retaining and positioning member 45. The retaining and positioning member is preferably formed from a resilient material, such as the same elastomeric material that is used to form the support member 42. However, the retaining and positioning member may be formed from any other desired material. The retaining and positioning member PALSpecificationsJ631324spei/klp can be provided to positively position the sponge 44 within the cavity 42a and to prevent the entry of dirt, water, and other contaminants into such cavity 42a. If desired, the retaining and positioning member 45 can be bonded or otherwise secured to the support ring 43.

Lastly, the centre bearing assembly 20 includes an annular bearing, indicated generally at 46, for rotatably supporting the first driveshaft section 17 thereon. The annular bearing 46 includes an outer race 46a that is supported on the support ring 43, an inner race 46b that engages the first driveshaft section 17, and a plurality of balls 46c disposed between the outer race 46a and the inner race 46b so that the inner race 46b is supported for rotation relative to the outer race 46a. Thus, the first driveshaft section 17 is supported for rotation by the centre bearing assembly As mentioned above, the sponge 44 may be formed from any material that is capable of absorbing or otherwise retaining a quantity of a fluid therein. In the preferred embodiment, the sponge 44 contains a quantity of a rheological fluid. As used herein, the term "rheological fluid" refers to a fluid that exhibits a change in its ability to flow or shear in the presence or upon the application of an appropriate energy field. In the preferred embodiment, the rheological fluid is a magneto-rheological (MR) fluid that is responsive to the presence of a magnetic field for changing its ability to flow or shear. MR fluids are formed of magnetisable particles, such as carbonyl iron, in a fluid carrier, such as a silicone oil. When exposed to a magnetic field, the particles align and reduce the ability of the fluid to flow. The shear resistance of the MR fluid is a function of the magnitude of the applied magnetic field. MR fluids are preferred for use in this invention because they are capable of generating relatively high fluid shear stresses and can be controlled using power supplies that are normally available in vehicles. TRW MR fluid, which is commercially available from TRW, Inc., is an example of one known theological fluid that has been found suitable for use in this invention. However, other rheological fluids can also be used in accordance with this invention. For example, electro-rheological (ER) fluids that are responsive to the presence of electrical energy (such as voltage or current) may also be used.

A control circuit, indicated generally at 50 in Fig. 3, is provided for selectively generating and applying an energy field to the rheological fluid contained within the sponge 44. The specific nature of the control circuit 50 will depend upon the particular type of rheological fluid that is selected for use. In the preferred embodiment, where the rheological fluid is an MR fluid, the control circuit includes one or more electromagnetic coils 51 that are provided within the centre bearing assembly 20 adjacent to the sponge 44.

The electromagnetic coil 51 is conventional in the art and is composed of a winding of an electrical conductor having leads 51a and 51b that extend therefrom through to a source of electrical power, such as an electrical current generator 52. In a manner that is known in the art, when a closed electrical circuit is established through the leads 51 a and 5 lb between the electromagnetic coil 51 and the source of current controller 52, electrical current flows through the coil 51. As a result, a magnetic field is generated by the electromagnetic coil 51.

PALSpecifications/631324specilklp The electromagnetic coil 51 may be arranged in any manner such that when it is energised, a magnetic field is applied to the MR fluid contained in the sponge 44. The electromagnetic coil 51 is preferably arranged so that the applied magnetic field is generally uniform throughout the sponge 44. In the illustrated embodiment, the coil 51 is disposed between the bracket 41 and the support member 42. However, the coil 42 may be located at any desired position relative to the bracket 41 and the support member 43.

By varying the magnitude of the electrical current that is supplied to the electromagnetic coil 51, the strength of the magnetic field that is applied to the MR fluid in the sponge 44 can be varied. As a result, the resistance to flow or shear of the MR fluid, which affects the vibration dampening characteristics of the support member 42, can be varied. To accomplish this, the control circuit 50 also includes a controller 53 that controls the operation of the current controller 52. The controller 53 is conventional in the art and may be embodied as any microprocessor or other programmable controller that is responsive to a signal from one or more sensors 54 for controlling the operation of the current generator 52. The sensor 54 is also conventional in the art and is adapted to generate an electrical signal that is representative of an operating condition of the vehicle. For example, some of the vehicle operating conditions that can be monitored by the sensor 54 can include ambient temperature, vehicle speed, vehicle acceleration, rotational speed of the first driveshaft section 17, angular displacement of the first driveshaft section 17, radial acceleration of the centre bearing assembly 20, axial acceleration of the centre bearing assembly 20, radial displacement of the centre bearing assembly 20, and axial displacement of the centre bearing assembly 20. However, any operating condition or group of conditions of the vehicle may be sensed and used to control the vibration dampening characteristics of the support member The controller 53 is programmed to periodically or continuously read the electrical signals from the sensor 54 and to generate an electrical control signal in response to a preprogrammed algorithm. The algorithm that is used by the controller 53 can be easily derived using known vibration data or by testing on the vehicle. For example, by measuring the amount of vibration that is generated for given value of the sensed operating condition, a look-up table can be created that correlates the value of the sensed operating condition with a value for the control signal that will minimise the generation of such vibration. The same procedure can be followed when two or more operating conditions are sensed. The current generator 52 is also conventional in the art and is responsive to the output signal from the controller 53 for generating a corresponding electrical current to the coil 51, which generates the magnetic field in response thereto. Thus, it can be seen that the magnitude of the output signal generated by the controller 53 determines the magnitude of the electromagnetic field generated by the electromagnetic coil 51 and, thus, varies the flow or shear characteristics of the MR fluid contained in the sponge 44. The vibration dampening characteristics of the support member 42 can, therefore, be continuously varied according to the control algorithm and the information provided by the sensor 54.

PALSpecifhions/63l324specikdp I I In accordance with the provisions of the patent statutes, the principle and mode of operation of this invention have been described in its preferred embodiment. However, it should be noted that this invention may be practiced otherwise than as specifically illustrated and described without departing from its spirit or scope.

PALSpecificaionsB31 324specdl

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Claims

1. A centre bearing assembly adapted to support a shaft for rotation relative to a support surface comprising: a bearing adapted to support a shaft for rotation; a bracket adapted to be supported on a support surface; and a sponge retaining a quantity of a fluid therein, said sponge being disposed between said bearing and said bracket.

2. The centre bearing assembly defined in Claim 1 wherein sponge is formed from an open cell foam material.

3. The centre bearing assembly defined in Claim 1 wherein said sponge contains a quantity of a rheological fluid, and further including a control circuit for selectively applying an energy field to said rheological fluid contained within said sponge.

4. The centre bearing assembly defined in Claim 3 further including a sensor that generates a signal that is representative of a sensed condition, and wherein said control circuit is responsive to said sensor signal for controlling the application of said energy field to said rheological fluid.

The centre bearing assembly defined in Claim 1 wherein said sponge contains a quantity of a magneto-rheological fluid, and further including a control circuit for selectively applying a magnetic energy field to said magneto-rheological fluid contained within said sponge.

6. The centre bearing assembly defined in Claim 5 further including a sensor that generates a signal that is representative of a sensed condition, and wherein said control circuit is responsive to said sensor signal for controlling the application of said magnetic energy field to said magneto-rheological fluid.

7. The centre bearing assembly defined in Claim 6 wherein said control circuit includes an electromagnetic coil disposed adjacent to said sponge.

8. The centre bearing assembly defined in Claim 1 further including an elastomeric support member disposed between said bearing and said bracket, and wherein said sponge is disposed within a portion of said support member.

9. The centre bearing assembly defined in Claim 8 wherein said support member has a cavity formed therein, and wherein said sponge is disposed within said cavity.

The centre bearing assembly defined in Claim 9 further including a retaining and positioning member disposed within said cavity.

11. A centre bearing assembly substantially as hereinbefore described with reference to the accompanying drawings. Dated 31 March, 2003 Dana Corporation Patent Attorneys for the Applicant/Nominated Person SPRUSON FERGUSON PALSpecificationsS631324speci/kip